JPH04266603A - Control circuit for distributing pressure medium flow regardless of load - Google Patents
Control circuit for distributing pressure medium flow regardless of loadInfo
- Publication number
- JPH04266603A JPH04266603A JP3301496A JP30149691A JPH04266603A JP H04266603 A JPH04266603 A JP H04266603A JP 3301496 A JP3301496 A JP 3301496A JP 30149691 A JP30149691 A JP 30149691A JP H04266603 A JPH04266603 A JP H04266603A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- conduit
- consumer
- balancer
- directional control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 10
- 230000001105 regulatory effect Effects 0.000 claims description 18
- 230000009467 reduction Effects 0.000 claims description 14
- 230000008859 change Effects 0.000 abstract description 9
- 230000000694 effects Effects 0.000 abstract description 7
- 230000009471 action Effects 0.000 abstract description 6
- 230000007423 decrease Effects 0.000 description 3
- 230000007935 neutral effect Effects 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000036316 preload Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010348 incorporation Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
- F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/35—Directional control combined with flow control
- F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/75—Control of speed of the output member
Abstract
Description
【0001】0001
【産業上の利用分野】本発明は、液圧式の1つのポンプ
に接続されて液力エネルギーを消費する複数の消費器に
圧力媒体流を荷重に無関係に分配するための制御回路で
あって、消費器がそれぞれ中間位置で絞り作用を生ぜし
める方向制御弁によって操作可能であり、方向制御弁の
上流側に方向制御弁への圧力媒体の流れを規定する圧力
バランサーを接続してあり、圧力バランサーが方向制御
弁の上流側の圧力及び方向制御弁の下流側の圧力から導
かれた第1の圧力差並びに、ポンプ圧力及び最大の負荷
圧力から導かれた第2の圧力差に関連して作動可能であ
る形式のものに関する。BACKGROUND OF THE INVENTION The present invention relates to a control circuit for load-independent distribution of a pressure medium flow to a plurality of consumers connected to a hydraulic pump and consuming hydraulic energy. The consumers can each be operated by a directional control valve which produces a throttling effect in an intermediate position, and a pressure balancer is connected upstream of the directional control valve to regulate the flow of pressure medium to the directional control valve. operates in conjunction with a first pressure difference derived from the pressure upstream of the directional control valve and the pressure downstream of the directional control valve, and a second pressure difference derived from the pump pressure and the maximum load pressure. Concerning the types of things that are possible.
【0002】0002
【従来の技術】前記形式の制御回路はドイツ連邦共和国
特許出願公告第3422165号公報により公知であり
、需要流調整装置と組み合わされている。このためにポ
ンプが通常は吐出容積調整装置を有しており、吐出容積
調整装置が需要流を調整する。需要流調整装置が、消費
器によって必要とされるエネルギーに関連してポンプの
吐出容積調整装置に作用する。従って、実際に必要な圧
力媒体量がポンプによって吐出され、これによって循環
損失及び絞り損失が避けられる。BACKGROUND OF THE INVENTION A control circuit of the above type is known from German Patent Application No. 34 22 165 and is combined with a demand flow regulator. For this purpose, the pump usually has a delivery volume regulator, which regulates the demand flow. A demand flow regulator acts on the pump's delivery volume regulator in relation to the energy required by the consumer. Therefore, the actually required amount of pressure medium is delivered by the pump, thereby avoiding circulation losses and throttling losses.
【0003】所属の方向制御弁が閉鎖位置を占めている
ことによって消費器が作動せしめられない場合には、ポ
ンプはもっぱら漏れオイルのみを吐出し、すなわち吐出
容積の最小の調節位置にあり、吐出容積の大きさ若しく
は吐出圧力の大きさは需要流調整装置に作用する調整ば
ねによって規定される。需要流調整装置は2つの制御圧
力室を有しており、一方の制御圧力室がポンプ圧力によ
って負荷され、かつ逆向きに作用する制御圧力室が最大
の消費器圧力及び調整ばねによって負荷され、調整ばね
が例えば20バールの圧力に相当するばね力を生ぜしめ
るように構成されている。If the consumer is not activated because the associated directional control valve is in the closed position, the pump exclusively discharges leakage oil, that is to say in the position of minimum adjustment of the delivery volume, The magnitude of the volume or the magnitude of the discharge pressure is determined by a regulating spring acting on the demand flow regulating device. The demand flow regulating device has two control pressure chambers, one control pressure chamber being loaded with the pump pressure and an oppositely acting control pressure chamber being loaded with the maximum consumer pressure and a regulating spring; The adjustment spring is designed to produce a spring force corresponding to a pressure of, for example, 20 bar.
【0004】消費器が作動させられず、かつ制御ピスト
ンが消費器に所属の方向制御弁内で零位置にある間、ポ
ンプは需要流調整装置に作用するポンプ圧力が需要流調
整装置の逆の側のばねとバランスする程度にのみ圧力媒
体を吐出する。While the consumer is not activated and the control piston is in the null position in the directional control valve associated with the consumer, the pump is operated such that the pump pressure acting on the demand flow regulator is opposite to the demand flow regulator. Pressure medium is discharged only to the extent that it balances with the side springs.
【0005】消費器の上流側に接続されている1つの方
向制御弁の制御ピストンの移動によって、該消費器とポ
ンプとが接続され、ポンプ圧力が消費器まで伝達される
。この場合、方向制御弁内で制御ピストンの移動によっ
て開放された開口が測定絞りとして作用する。同時に、
荷重圧力、すなわち作動された方向制御弁と制御された
消費器との間の導管内の圧力が制御圧力導管を介して需
要流調整装置のばね側を負荷して、これによってポンプ
が吐出容積増大の信号を得て、吐出容積、ひいてはポン
プ圧力を増大させる。By movement of the control piston of one directional control valve connected upstream of the consumer, the consumer and the pump are connected and the pump pressure is transmitted to the consumer. In this case, the opening opened in the directional control valve by the movement of the control piston acts as a measuring throttle. at the same time,
The load pressure, i.e. the pressure in the line between the actuated directional control valve and the controlled consumer, loads the spring side of the demand flow regulator via the control pressure line, so that the pump increases its delivery volume. signal to increase the discharge volume and thus the pump pressure.
【0006】ポンプ圧力の増大に基づき、消費器が運動
させられ、測定絞り内に圧力差Δpが生ぜしめられる。
系内のバランスは、方向制御弁内の圧力差Δpが需要流
調整装置のばねプレロードに相応する場合に生じる。こ
れによって、ポンプの吐出流が自動的に需要流に適合す
る。消費器に所属する方向制御弁、若しくは方向制御弁
の制御ピストンがハンドレバーを介して操作され、ハン
ドレバーの調節距離が消費器に達する吐出媒体の量に比
例しており、この場合方向制御弁内の圧力差Δpが常に
コンスタントである。従って測定絞りを通って常に、制
御ピストンの位置にのみ関連てかつ消費器の荷重圧力に
は無関係な圧力媒体流が流れる。Due to the increase in pump pressure, the consumer is moved and a pressure difference Δp is created in the measuring throttle. A balance in the system occurs if the pressure difference Δp in the directional control valve corresponds to the spring preload of the demand flow regulator. This automatically adapts the pump discharge flow to the demand flow. The directional control valve belonging to the consumer, or the control piston of the directional control valve, is actuated via a hand lever, the adjustment distance of which is proportional to the amount of delivery medium reaching the consumer, in which case the directional control valve The pressure difference Δp within is always constant. A flow of pressure medium therefore always flows through the measuring throttle, which is dependent only on the position of the control piston and is independent of the load pressure of the consumer.
【0007】需要流調整装置は、最大の荷重圧力を交換
弁列によって検出して需要流調整装置に伝達することに
よって多数の消費器においても機能する。しかしながら
、制御される多数の消費器においては需要流調整装置は
常にそのつど最大の荷重圧力に応動して、その結果荷重
圧力の低い消費器の方向制御弁の測定絞りとして作用す
る制御縁開口が新たに調整され、増大するポンプ吐出量
に基づき増大する大きな圧力差が補償され、1つの消費
器を衝撃的に強く負荷する場合にも多数の消費器の運動
速度が一様にされなければならない。さらに、ポンプの
最大の吐出容積がすでに達せられている場合にも、異な
る消費器の運動速度の比が互いに維持されねばならない
。このために、ポンプと方向制御弁との間の導管内に圧
力バランサーとして作用する補助弁が組み込まれており
、補助弁の閉鎖方向で負荷される制御圧力室が方向制御
弁の前の圧力によって負荷されており、補助弁の開放方
向で負荷する制御圧力室が方向制御弁と消費器供給通路
との間の圧力、すなわち所属の消費器圧力によって負荷
されている。閉鎖方向で作用する補助圧力室がそのつど
最大の荷重圧力で負荷される消費器の圧力で負荷され、
かつ開放方向で作用する補助圧力室がポンプの吐出導管
内の圧力で負荷される。従って2つの圧力差が生ぜしめ
られ、この場合第1の圧力差が所属の消費器の荷重圧力
と中間位置で絞り作用を有する方向制御弁の前の圧力と
によって生じ、かつ第2の圧力差がポンプ吐出圧力と最
大に負荷される消費器の荷重圧力とによって生じる。も
ちろん、圧力差を直接に圧力バランサーにおいて生ぜし
めるのではなく、前以て生ぜしめて例えば制御圧力の形
式で圧力バランサーに導き、そこでばねの力に抗して作
用させることも可能である。いずれの場合にも、圧力バ
ランサーが所属の消費器圧力と最大の荷重圧力との圧力
差を補償する。従って消費器流が個別の測定絞り開口の
横断面に相応して生ぜしめられる。The demand flow regulator also functions in a large number of consumers by detecting the maximum load pressure by means of an exchange valve train and transmitting it to the demand flow regulator. However, in the case of a large number of controlled consumers, the demand flow regulating device always responds to the maximum load pressure in each case, so that the control edge opening, which acts as a measuring throttle for the directional control valve of the consumer with lower load pressure, is Due to the newly adjusted and increasing pump output, the increasing pressure differences must be compensated and the speed of movement of the numerous consumers must be made uniform even when one consumer is subjected to a shockingly high load. . Furthermore, the ratio of the speeds of movement of the different consumers must be maintained with respect to each other even if the maximum displacement of the pump has already been reached. For this purpose, an auxiliary valve is integrated in the conduit between the pump and the directional control valve, acting as a pressure balancer, so that the control pressure chamber, which is loaded in the closing direction of the auxiliary valve, is affected by the pressure in front of the directional control valve. The control pressure chamber, which is loaded and loaded in the opening direction of the auxiliary valve, is loaded by the pressure between the directional control valve and the consumer supply channel, ie the associated consumer pressure. the auxiliary pressure chambers acting in the closing direction are loaded with the pressure of the consumer, which is loaded with the maximum load pressure in each case;
The auxiliary pressure chamber, which acts in the opening direction, is then loaded with the pressure in the delivery line of the pump. Two pressure differences are therefore created, a first pressure difference being created by the load pressure of the associated consumer and the pressure upstream of the directional control valve with a throttling action in an intermediate position, and a second pressure difference. is caused by the pump discharge pressure and the load pressure of the most loaded consumer. Of course, it is also possible not to create the pressure difference directly in the pressure balancer, but to create it in advance, for example in the form of a controlled pressure, to the pressure balancer and to act there against the force of the spring. In both cases, a pressure balancer compensates for the pressure difference between the associated consumer pressure and the maximum load pressure. The consumer flow is therefore generated in accordance with the cross section of the individual measuring throttle opening.
【0008】従って量調整装置を備えた方向制御弁は、
ポンプによって吐出される媒体流が消費器によって受容
される媒体量に相応しているかぎりにおいて、ポンプ流
を荷重に無関係に制御ピストンの絞り開口の割合で分配
する。消費器流がポンプの最大の吐出流を越えると、最
大の吐出流がそれぞれの消費器に所属する方向制御弁の
開かれる割合で消費器に分配される。[0008] Therefore, a directional control valve equipped with a quantity adjusting device has the following characteristics:
As long as the medium flow delivered by the pump corresponds to the medium quantity received by the consumer, the pump flow is distributed in proportion to the throttle opening of the control piston, regardless of the load. If the consumer flow exceeds the maximum delivery flow of the pump, the maximum delivery flow is distributed to the consumers at the rate at which the directional control valves belonging to the respective consumers are opened.
【0009】このような回路を例えば掘削機に使用した
場合、例えば同時に制御された2つの調節シリンダによ
って生ぜしめられる軌道カーブがいかなる場合にも維持
され、かつ最大のポンプ吐出流の越えられる際には軌道
カーブを描く調節シリンダの速度のみが減少させられる
。制御される消費器の運動速度の比は、所属の操作され
た方向制御弁の絞り開口の比に関連している。この場合
、圧力差はすべての方向制御弁において同じであり、需
要流調整装置の調整圧力差に相応している。消費器の運
動速度の比において変化を行うためには、方向制御弁へ
の操作員による手動的な作用が必要である。特に軌道カ
ーブを高い精度で走行したい場合には、著しい熟練が必
要である。When such a circuit is used, for example, in an excavator, it can be ensured that the trajectory curve produced, for example, by two simultaneously controlled adjusting cylinders, is maintained in all cases and that when the maximum pump delivery flow is exceeded, Only the speed of the adjusting cylinder that describes the trajectory curve is reduced. The ratio of the movement speeds of the controlled consumers is related to the ratio of the throttle openings of the associated actuated directional control valves. In this case, the pressure difference is the same for all directional control valves and corresponds to the regulating pressure difference of the demand flow regulating device. Manual action by the operator on the directional control valve is required to effect a change in the rate of movement of the consumer. In particular, if you want to travel around track curves with high precision, a great deal of skill is required.
【0010】0010
【発明が解決しようとする課題】本発明の課題は冒頭に
述べた形式の制御回路を改善して、消費器運動の速度比
の変化が簡単な手段で方向制御弁への作用に無関係に行
われるようにすることである。SUMMARY OF THE INVENTION The object of the invention is to improve a control circuit of the type mentioned at the outset so that the speed ratio of the consumer movement can be varied by simple means and independently of the action on the directional control valve. The aim is to make sure that the
【0011】[0011]
【課題を解決するための構成】前記課題を解決するため
に本発明の構成では、少なくとも1つの圧力バランサー
で圧力差が調節できるようになっている。[Structure for Solving the Problems] In order to solve the above problems, the structure of the present invention is such that the pressure difference can be adjusted by at least one pressure balancer.
【0012】0012
【発明の効果】前記構成によって当該の圧力バランサー
における圧力バランスが移され、ひいては圧力バランサ
ーと方向制御弁との間の圧力が変化し、これによって方
向制御弁における圧力差の変化、ひいては圧力媒体及び
消費器速度の変化が生ぜしめられる。本発明の重要な思
想は、少なくとも1つの圧力バランサーにおける調整圧
力差が意図的に調節可能であり、消費器の運動速度の比
が制御できるようにすることにある。Effects of the Invention With the above configuration, the pressure balance in the pressure balancer concerned is shifted, and thus the pressure between the pressure balancer and the directional control valve is changed, which causes a change in the pressure difference in the directional control valve, and thus a change in the pressure medium and the directional control valve. A change in consumer speed is produced. An important idea of the invention is that the regulating pressure difference in the at least one pressure balancer is intentionally adjustable, so that the ratio of the speeds of movement of the consumer can be controlled.
【0013】本発明の有利な構成では、圧力バランサー
が所属の方向制御弁の後の圧力から導かれた圧力、及び
ポンプ圧力から導かれた圧力によって開放方向へかつ、
方向制御弁の前の圧力から導かれた圧力、及びすべての
消費器の最大の出力圧力から導かれた圧力によって閉鎖
方向へ負荷されており、圧力バランサーに圧力のための
作用面が設けられており、作用面に圧力導管が通じてお
り、少くとも1つの圧力導管内に、圧力に影響を及ぼす
装置が接続されている。吐出流分配の任意の変化のため
に、圧力バランサーにおけるバランスを規定する4つの
作用面の1つが意図的に変えられ、これによって圧力バ
ランサーにおける開放力若しくは閉鎖力が制御され、ひ
いては方向制御弁の制御ピストンによって形成された測
定絞りを通る圧力媒体流の通過流が最終的に制御される
。In an advantageous embodiment of the invention, the pressure balancer is moved in the opening direction by the pressure derived from the pressure after the associated directional control valve and by the pressure derived from the pump pressure;
It is loaded in the closing direction by the pressure derived from the pressure in front of the directional control valve and by the pressure derived from the maximum output pressure of all the consumers, and the pressure balancer is provided with an active surface for the pressure. A pressure conduit leads to the working surface, and a device for influencing the pressure is connected in at least one pressure conduit. For any change in the discharge flow distribution, one of the four working surfaces defining the balance in the pressure balancer is intentionally changed, which controls the opening or closing force in the pressure balancer and thus the directional control valve. The passage of the pressure medium flow through the measuring throttle formed by the control piston is ultimately controlled.
【0014】本発明の有利な構成では、圧力に影響を及
ぼす装置が圧力減少弁として構成されている。圧力減少
弁は所定値に設定されていてよく、若しくは本発明の有
利な別の構成では調節可能である。圧力減少弁を調節可
能に構成してある場合には、調節が遠隔操作によって、
例えば電気的に行われ、その結果圧力減少弁を備えた導
管内に生ぜしめる目標値が電気的な調整装置を用いて操
作員によって任意に変えられる。このような変化をプロ
グラム制御によって行うことも可能である。[0014] In an advantageous embodiment of the invention, the device for influencing the pressure is designed as a pressure reduction valve. The pressure reduction valve can be set at a predetermined value or, in an advantageous further embodiment of the invention, can be adjusted. If the pressure reduction valve is configured to be adjustable, the adjustment can be done remotely.
For example, this can be done electrically, so that the setpoint value produced in the line with the pressure reduction valve can be varied at will by the operator using an electrical regulating device. It is also possible to make such changes under program control.
【0015】本発明の別の有利な構成では、圧力に影響
を及ぼす装置が絞りを有しており、絞りの下流側から排
出導管が分岐しており、この分岐導管内に絞りが設けら
れており、この絞りの下流側に圧力制限弁が接続されて
いる。このような絞りの組込によって圧力減少弁と同じ
機能が得られる。圧力に影響を及ぼす装置がポンプに通
じる導管内に配置されており、この導管が1つの消費器
の圧力バランサーの作用面に通じているか、若しくは圧
力に影響を及ぼす装置が最大の消費器圧力を導く導管内
に配置されており、この導管が1つの消費器の圧力バラ
ンサーの作用面に通じている。圧力に影響を及ぼす装置
をポンプに通じる導管内及び最大の消費器圧力を導く導
管内に配置することも可能である。方向制御弁を通る圧
力媒体の通過流量の制御は、原理的には方向制御弁の応
動圧力、すなわち方向制御弁の前及び後ろの圧力を制御
することによっても行われる。[0015] In a further advantageous embodiment of the invention, the device for influencing the pressure has a restriction, and downstream of the restriction, a discharge line branches off, in which the restriction is provided. A pressure limiting valve is connected downstream of this throttle. The incorporation of such a restriction provides the same function as a pressure reduction valve. Either the pressure influencing device is arranged in a conduit leading to the pump and this conduit leads to the working surface of a pressure balancer of one consumer, or the pressure influencing device It is arranged in a leading conduit which leads to the working surface of the pressure balancer of one consumer. It is also possible to arrange devices for influencing the pressure in the conduit leading to the pump and in the conduit leading to the maximum consumer pressure. In principle, the flow rate of the pressure medium through the directional control valve can also be controlled by controlling the responsive pressure of the directional control valve, that is to say the pressure in front and behind the directional control valve.
【0016】[0016]
【実施例】液力式のポンプ1が調節シリンダ2内でばね
3の力に抗して移動可能な調節ピストン4を用いて吐出
量を変えられるようになっている。ポンプ1は圧力媒体
をタンク5から吸い込み、吐出導管6内へ吐出するよう
になっており、吐出導管が分岐供給導管7,8に分岐し
ている。分岐供給導管7,8は圧力バランサー9,10
に通じており、圧力バランサーが2ポート2位置方向制
御弁として構成されている。圧力バランサー9,10の
下流側に、ばねによって中立位置に保たれ中立位置で絞
り作用を生ぜしめる方向制御弁11,12を接続してあ
り、方向制御弁が実施例ではシリンダ・ピストン装置と
して構成された2つの側から負荷可能な消費器13,1
4を制御するために用いられる。DESCRIPTION OF THE PREFERRED EMBODIMENTS A hydraulic pump 1 is adapted to vary the delivery volume by means of an adjusting piston 4 movable in an adjusting cylinder 2 against the force of a spring 3. The pump 1 is adapted to suck pressure medium from a tank 5 and discharge it into a discharge conduit 6, which branches into branch supply conduits 7, 8. Branch supply conduits 7, 8 are connected to pressure balancers 9, 10
The pressure balancer is configured as a 2-port, 2-position directional control valve. Connected to the downstream side of the pressure balancers 9, 10 are directional control valves 11, 12 which are held in a neutral position by springs and produce a throttling action in the neutral position, and the directional control valves are configured as cylinder-piston devices in the embodiment. A consumer 13,1 that can be loaded from two sides
Used to control 4.
【0017】この目的のために、方向制御弁11が導管
15,16を介して消費器13に接続されており、方向
制御弁12が導管17,18を介して消費器14に接続
されている。消費器13,14の制御された状態では、
それぞれ圧力を導く導管15若しくは16,17若しく
は18が導管19若しくは20に接続されており、ひい
てはこの導管が消費器の負荷圧力を導く。導管19,2
0は分岐導管19a,20aを有しており、この分岐導
管が交換弁(切換弁)21に開口している。分岐導管1
9a,20a内に生じる高い方の圧力、すなわち消費器
13,14の高い方の圧力が交換弁21から導管22を
介して伝達されるようになっており、この導管が需要流
調整弁23の一方の端面に通じている。需要流調整弁2
3は導管6aに接続されており、この導管は吐出導管6
から分岐している。需要流調整弁23から導管6aが調
節ピストン4のばね3と逆の端面側で調節シリンダ2に
通じている。導管6aからは、さらに導管6cが分岐し
ており、この導管6cは需要流調整弁23の他方の端面
に通じている。一方の端面にはさらに圧縮ばね23aが
配置されている。需要流調整弁23は3つの切換位置を
有している。第1の切換位置では導管6aが導管6b、
ひいては調節シリンダ2に接続されている。第2の切換
位置では両方の導管6a,6bが無圧のタンク5に接続
されている。第3の切換位置では導管6aが遮断されて
おり、導管6bがタンク5に接続されている。For this purpose, a directional control valve 11 is connected via conduits 15, 16 to a consumer 13, and a directional control valve 12 is connected via conduits 17, 18 to a consumer 14. . In the controlled state of the consumers 13, 14,
A pressure line 15 or 16, 17 or 18, respectively, which carries the pressure is connected to the line 19 or 20, which in turn carries the load pressure of the consumer. Conduit 19, 2
0 has branch conduits 19a, 20a, which open to an exchange valve (switching valve) 21. Branch conduit 1
The higher pressure occurring in 9a, 20a, i.e. the higher pressure of the consumers 13, 14, is transmitted from the exchange valve 21 via a conduit 22, which conduit is connected to the demand flow regulating valve 23. It leads to one end face. Demand flow adjustment valve 2
3 is connected to a conduit 6a, which is a discharge conduit 6.
It is branching from. A conduit 6 a leads from the demand flow regulating valve 23 to the regulating cylinder 2 on the end side of the regulating piston 4 facing away from the spring 3 . A conduit 6c further branches from the conduit 6a, and this conduit 6c communicates with the other end face of the demand flow regulating valve 23. A compression spring 23a is further arranged on one end face. The demand flow regulating valve 23 has three switching positions. In the first switching position, the conduit 6a is replaced by the conduit 6b,
In turn, it is connected to the adjusting cylinder 2. In the second switching position, both lines 6a, 6b are connected to the pressureless tank 5. In the third switching position, conduit 6a is blocked and conduit 6b is connected to tank 5.
【0018】各圧力バランサー9,10はそれぞれ4つ
の作用面を有しており、2つの作用面が圧力バランサー
の開放方向に作用するように配置されており、ほかの2
つの作用面が圧力バランサーの閉鎖方向に作用するよう
に配置されている。圧力バランサー9には導管19から
分岐した導管19bが開放方向に作用する両方の作用面
に通じている。開放方向に作用する両方の作用面には、
分岐供給導管7から分岐した導管7aが通じている。圧
力バランサー9の閉鎖方向に作用する作用面に、導管2
2から分岐する導管22a及び導管24が通じており、
この場合導管24は導管25から分岐しており、導管2
5は圧力バランサー9を方向制御弁11に接続している
。Each pressure balancer 9, 10 has four working surfaces, two working surfaces are arranged so as to act in the opening direction of the pressure balancer, and the other two working surfaces are arranged so as to act in the opening direction of the pressure balancer.
The two active surfaces are arranged to act in the closing direction of the pressure balancer. In the pressure balancer 9, a conduit 19b branching off from the conduit 19 leads to both active surfaces acting in the opening direction. Both working surfaces acting in the opening direction have
A conduit 7a branched from the branch supply conduit 7 communicates therewith. On the working surface of the pressure balancer 9 acting in the closing direction, the conduit 2
A conduit 22a and a conduit 24 branching from 2 communicate with each other,
In this case, the conduit 24 is branched from the conduit 25;
5 connects the pressure balancer 9 to the directional control valve 11.
【0019】圧力バランサー9に類似して、第2の消費
器の圧力バランサー10が4つの作用面を有しており、
これらのうち2つの作用面が開放方向に作用しておりか
つ残りの2つの作用面が閉鎖方向に作用している。導管
20から分岐する導管20b及び導管8から分岐する導
管8aが圧力バランサー10の閉鎖方向に作用する作用
面に通じている。閉鎖方向に作用する作用面には、導管
22から分岐する導管22b及び導管26が通じており
、この場合導管26は導管27から分岐しており、導管
27は圧力バランサー10を方向制御弁12に接続して
いる。導管7a及び導管22b内には圧力減少弁28,
29が配置されている。Similar to the pressure balancer 9, the pressure balancer 10 of the second consumer has four active surfaces;
Two of these active surfaces act in the opening direction and the remaining two active surfaces act in the closing direction. A conduit 20b branching off from the conduit 20 and a conduit 8a branching off from the conduit 8 lead to an active surface of the pressure balancer 10 acting in the closing direction. A line 22b and a line 26, which branch off from the line 22, are connected to the active surface acting in the closing direction, which in this case branches off from a line 27, which connects the pressure balancer 10 to the directional valve 12. Connected. In conduit 7a and conduit 22b there is a pressure reduction valve 28,
29 are arranged.
【0020】前述の制御装置の作用形式は次に述べる通
りである:消費器13,14の非作動状態では、方向制
御弁は中立位置にあり、従って導管15,16;17,
18並びに19,19a,19b;20,20a,20
b及び22は無圧である。ポンプは、ばね3が調節ピン
4をポンプの最大吐出容積に相当する位置に常にもたら
そうとするように構成されている。ポンプ1の吐出開始
時には方向制御弁11、12の閉じられていることに基
づき導管6内に圧力が形成される。この圧力は導管6a
,6cを介して必要量調整装置23の第2の端面に伝達
される。必要量調整装置23が、例えば20バールの圧
力に設定されたばね23aの力に基づき第3の切換位置
にあり、この切換位置では導管6bがタンク5に接続さ
れている。ポンプ吐出圧力の上昇に伴って、必要量調整
装置が図面で見て右側へ移動して最終的に導管6aを導
管6bに接続し、ひいてはポンプ1の吐出容積を減少さ
せる。必要量調整装置にはばね力とポンプ吐出圧力との
間の圧力バランスが生じている。従って、ポンプ1は消
費器の非作動状態ではもっぱら小さい圧力媒体流を吐出
して、20バールの吐出圧力を維持している。The mode of operation of the control device described above is as follows: in the inactive state of the consumers 13, 14, the directional control valves are in the neutral position, so that the conduits 15, 16; 17,
18 and 19, 19a, 19b; 20, 20a, 20
b and 22 are pressureless. The pump is constructed in such a way that the spring 3 always tends to bring the adjusting pin 4 into a position corresponding to the maximum displacement of the pump. When the pump 1 begins to pump, a pressure builds up in the conduit 6 because the directional control valves 11, 12 are closed. This pressure is in conduit 6a
, 6c to the second end face of the required amount adjustment device 23. Due to the force of a spring 23a set to a pressure of, for example, 20 bar, the demand regulator 23 is in a third switching position, in which the line 6b is connected to the tank 5. As the pump delivery pressure increases, the required volume regulating device moves to the right in the drawing and finally connects the conduit 6a to the conduit 6b, thus reducing the delivery volume of the pump 1. A pressure balance occurs in the demand regulator between the spring force and the pump delivery pressure. The pump 1 therefore delivers only a small flow of pressure medium in the inactive state of the consumer to maintain a delivery pressure of 20 bar.
【0021】一方の方向制御弁11若しくは12、例え
ば方向制御弁11を所属の消費器の制御のために作動さ
せる場合には、方向制御弁内の制御ピストンが移動させ
られ、これによってポンプ1と消費器13とが接続され
、この場合任意に選択された横断面が開放され、所定の
圧力媒体流が消費器に供給され、ひいては消費器の所定
の運動速度が得られる。ポンプ圧力が負荷圧力を上回る
と、消費器13が運動させられ、圧力媒体の流れによっ
て方向制御弁11の自由な横断面に圧力差Δpが生ぜし
められる。自由な横断面は原理的には測定絞りとして作
用する。系内の圧力バランスは、測定絞りにおける圧力
差が需要流調整装置23のばね23のばねプレロードに
相応すると生じる。測定絞り開口の変化は、方向制御弁
における圧力差Δpの変化を生ぜしめ、圧力差の変化が
需要流調整装置23によって調整され、これによって方
向制御弁におけるコンスタントな圧力差が常に維持され
る。その結果、測定絞りを通って、負荷圧力に無関係な
コンスタントなもっぱら開口値(速度設定値)に関連し
た圧力媒体流が流れる。ポンプの吐出流が自動的に需要
流量に適合される。When one directional control valve 11 or 12, for example directional control valve 11, is to be activated for controlling the associated consumer, a control piston in the directional control valve is moved, so that pump 1 and A consumer 13 is connected, in which case an arbitrarily selected cross section is opened, and a defined flow of pressure medium is supplied to the consumer and thus a defined speed of movement of the consumer is achieved. When the pump pressure exceeds the load pressure, the consumer 13 is put into motion and a pressure difference Δp is created across the free cross section of the directional control valve 11 by means of the flow of pressure medium. In principle, the free cross section acts as a measuring aperture. A pressure balance in the system occurs if the pressure difference at the measuring throttle corresponds to the spring preload of the spring 23 of the demand flow regulator 23. A change in the measuring throttle opening causes a change in the pressure difference Δp across the directional control valve, and the change in pressure difference is adjusted by the demand flow regulating device 23, so that a constant pressure difference across the directional control valve is always maintained. As a result, a pressure medium flow flows through the measuring throttle that is constant and exclusively dependent on the opening value (speed setpoint), which is independent of the load pressure. The pump discharge flow is automatically adapted to the demand flow.
【0022】方向制御弁11と同時に方向制御弁12、
ひいては付加的に消費器14を制御する場合には、高い
方の負荷圧力、例えば消費器13の負荷圧力が交換弁2
1によって需要流調整装置23のばね側に導かれる。従
って、低い圧力で負荷される消費器14の方向制御弁1
2における圧力差が増大せしめられ、操作員によっる方
向制御弁の後調節が必要になり、これによって所望の消
費器速度が維持される。圧力差の変化を一様にするため
に、圧力バランサー9,10が設けられている。引き続
く監視に際し、圧力バランサーへの圧力減少弁28,2
9の作用は無視される。各圧力バランサー9,10には
2つの差圧力が形成される。第1の差圧力は、導管19
b若しくは20b内を導かれた負荷圧力を方向制御弁1
1若しくは12の上流側で導管24若しくは26内に生
じる圧力に対して相互接続することに基づき形成される
。第2の差圧力は、導管7a若しくは8a内に生じるポ
ンプ吐出圧力を導管22a若しくは22b内に生じる最
大の負荷圧力に対して相互接続することによって形成さ
れる。At the same time as the direction control valve 11, the direction control valve 12,
Therefore, if the consumer 14 is additionally controlled, the higher load pressure, for example the load pressure of the consumer 13, is applied to the exchange valve 2.
1 to the spring side of the demand flow adjustment device 23. Therefore, the directional control valve 1 of the consumer 14 is loaded with low pressure.
The pressure differential at 2 is increased, requiring subsequent adjustment of the directional control valve by the operator to maintain the desired consumer speed. Pressure balancers 9, 10 are provided to equalize changes in pressure difference. During subsequent monitoring, the pressure reduction valve 28,2 to the pressure balancer
The effect of 9 is ignored. Two differential pressures are created in each pressure balancer 9,10. The first differential pressure is in conduit 19
The load pressure guided through the direction control valve 1
1 or 12 is formed on the basis of an interconnection for the pressure occurring in the conduit 24 or 26 upstream. A second differential pressure is created by interconnecting the pump discharge pressure occurring in conduit 7a or 8a to the maximum load pressure occurring in conduit 22a or 22b.
【0023】この実施例においては、消費器13におけ
る負荷圧力が消費器14における負荷圧力より高いこと
から出発する。この高い負荷圧力が導管22aを介して
圧力バランサー9に伝達される。逆の側の導管19b内
にも同じ負荷圧力が生じているので、この圧力は上昇す
る。導管7a内にポンプ圧力が生じ、このポンプ圧力は
Δpだけ高められた最大の負荷圧力に相応している。こ
の圧力とは逆向きに、方向制御弁11の上流側で導管2
4内に生じる圧力が生じており、この圧力はポンプ吐出
圧力とほぼ同じ大きさである。これによって圧力バラン
サー9に圧力バランスが生じ、圧力バランサーが開かれ
たままである。In this embodiment, it is assumed that the load pressure at the consumer 13 is higher than the load pressure at the consumer 14. This high load pressure is transmitted to the pressure balancer 9 via the conduit 22a. Since the same load pressure is present in the conduit 19b on the opposite side, this pressure increases. A pump pressure is generated in line 7a, which pump pressure corresponds to the maximum load pressure increased by Δp. Opposite to this pressure, on the upstream side of the directional control valve 11, the conduit 2
4, which is approximately the same magnitude as the pump discharge pressure. This creates a pressure balance in the pressure balancer 9, which remains open.
【0024】第2の消費器14の圧力バランサー10は
導管22bを介して最大の負荷圧力で、すなわち消費器
13の負荷圧力で負荷される。従って、圧力バランサー
10にはアンバランスが生じ、その結果この圧力バラン
サーがいくらか閉鎖方向へ移動させられ、これによって
絞り作用を生ぜしめ、この絞り作用が導管27内の圧力
を所定の値に減少させ、この値は方向制御弁12内に所
定の圧力差Δp(実施例では20バール)の達成される
程度の大きさである。これにより方向制御弁11,12
の両方の測定絞りにとって圧力差Δpは同じであり、消
費器流は測定絞り開口の比と同じである。The pressure balancer 10 of the second consumer 14 is loaded via line 22b with the maximum load pressure, ie with the load pressure of the consumer 13. An imbalance therefore occurs in the pressure balancer 10, with the result that it is moved somewhat in the closing direction, thereby creating a throttling action which reduces the pressure in the conduit 27 to a predetermined value. , this value is such that a predetermined pressure difference Δp (20 bar in the exemplary embodiment) is achieved in the directional control valve 12. As a result, the directional control valves 11, 12
The pressure difference Δp is the same for both measuring throttles and the consumer flow is the same as the ratio of the measuring throttle openings.
【0025】消費器流の比、ひいては作業速度の比を測
定絞り開口の横断面に無関係に変えるために、本発明に
基づき圧力バランサーに作用する影響力が任意に制御可
能に変えられる。このことは一方若しくは両方の圧力バ
ランサーにおいて行われる。圧力減少弁28(定置に調
節され、若しくは所定の段階で調節可能若しくは電気的
に無段に調節可能に構成されていてよい)は、圧力を減
少させる調節位置に位置している間、導管7a内で、圧
力バランサー9に作用するポンプ吐出圧力を減少させ、
その結果圧力バランサー9が閉鎖方向へ作動し、これに
よって絞り作用が得られる。従って、導管25内に生じ
る圧力が導管7内に生じる圧力に対して低下し、負荷圧
力の変えられない状態で方向制御弁11における圧力差
Δpが減少し、ひいては消費器13の運動速度が減少す
る。In order to vary the ratio of the consumer flows and thus of the working speeds independently of the cross-section of the measuring throttle opening, according to the invention the influence force acting on the pressure balancer can be varied controllably at will. This can be done on one or both pressure balancers. The pressure reducing valve 28 (which may be configured to be fixedly adjustable or adjustable in predetermined steps or continuously adjustable electrically) is in the adjusting position where it reduces the pressure while the conduit 7a reduce the pump discharge pressure acting on the pressure balancer 9,
As a result, the pressure balancer 9 is actuated in the closing direction, resulting in a throttling effect. Therefore, the pressure occurring in the conduit 25 decreases with respect to the pressure occurring in the conduit 7, and the pressure difference Δp at the directional control valve 11 decreases, with the load pressure unchanged, and thus the speed of movement of the consumer 13 decreases. do.
【0026】導管22b内の圧力減少弁29は、圧力を
減少させる調節位置にあるかぎりにおいて、圧力バラン
サー10に作用する最大の出力圧力を減少させ、ひいて
は圧力バランサー10の開放方向へバランスを移す。こ
れによって圧力バランサー10に存在する絞り作用が(
消費器14が消費器13よりも小さい出力圧力を有して
いる場合に)減少させられ、あるいは消滅する。その結
果、導管27内の圧力が導管8内の圧力に対して全く減
少させられないか若しくはわずかしか減少させられず、
これによって消費器14の出力圧力の不変の状態で方向
制御弁12における圧力差、ひいては消費器14の運動
速度が増大する。The pressure reducing valve 29 in the conduit 22b reduces the maximum output pressure acting on the pressure balancer 10 and thus shifts the balance in the direction of opening the pressure balancer 10, insofar as it is in the adjustment position which reduces the pressure. This reduces the throttling effect present in the pressure balancer 10 (
(if the consumer 14 has a smaller output pressure than the consumer 13) or disappears. As a result, the pressure in conduit 27 is not reduced at all or only slightly relative to the pressure in conduit 8;
As a result, the pressure difference across the directional control valve 12 and thus the speed of movement of the consumer 14 increases with the output pressure of the consumer 14 unchanged.
【0027】圧力減少弁28,29の調節は手動で若し
くはプログラム制御に基づき行われる。導管19b,2
4,20b,26内に圧力減少弁、若しくは圧力に影響
を与える別の装置が設けられていてよいことは明らかで
ある。The adjustment of the pressure reduction valves 28, 29 can be done manually or under program control. Conduit 19b, 2
It is clear that pressure reducing valves or other devices influencing the pressure may be provided in 4, 20b, 26.
【0028】圧力減少弁の代わりに、絞り機構を設ける
ことも可能である。このような絞り機構は図2に示して
ある。導管7a内に圧力減少弁28の代わりに絞り30
が配置されている。絞り30の下流側で導管7aから排
出導管7bが分岐している。排出導管7b内には別の絞
り31が配置してあり、この絞りの下流側に圧力制限弁
32が接続されている。圧力制限弁32が開くと、圧力
媒体がタンク5内へ流れ、絞り30において圧力差が生
じる。この圧力差だけ減少したポンプ吐出圧力が圧力バ
ランサー9に作用せしめられる。圧力減少弁32はこの
実施例では閉鎖方向でばね力に加えて最大の出力圧力で
負荷されている。絞り30,31の絞り幅は、圧力制限
弁に開放方向で作用する圧力が最大の出力圧力よりも常
に大きくなっていて、圧力制限弁の開放が保証されるよ
うに規定されている。装置を停止させるためには、圧力
制限弁の調節可能なばねが強く緊縮され、圧力制限弁が
閉じられたままになる。[0028] Instead of a pressure reduction valve, it is also possible to provide a throttling mechanism. Such a diaphragm mechanism is shown in FIG. In the conduit 7a there is a restriction 30 instead of the pressure reducing valve 28.
is located. A discharge conduit 7b branches from the conduit 7a on the downstream side of the throttle 30. A further throttle 31 is arranged in the discharge conduit 7b, downstream of which a pressure limiting valve 32 is connected. When the pressure limiting valve 32 opens, pressure medium flows into the tank 5 and a pressure difference is created at the restriction 30. The pump discharge pressure reduced by this pressure difference is applied to the pressure balancer 9. In this embodiment, the pressure reduction valve 32 is loaded with a spring force and a maximum output pressure in the closing direction. The aperture widths of the throttles 30 and 31 are determined so that the pressure acting on the pressure limiting valve in the opening direction is always greater than the maximum output pressure, and opening of the pressure limiting valve is guaranteed. To shut down the device, the adjustable spring of the pressure limiting valve is tightened tightly and the pressure limiting valve remains closed.
【図1】2つの消費器を備えた本発明に基づく制御回路
。FIG. 1 shows a control circuit according to the invention with two consumers.
【図2】本発明に基づく別の実施例の制御回路。FIG. 2 shows a control circuit of another embodiment according to the invention.
1 ポンプ、 2 調節シリンダ、 3 ば
ね、 4 調節ピストン、 5タンク、 6
吐出導管、 6a,6b,6c 導管、 7
分岐供給導管、7a 導管、 7b 排出導管
、 8 分岐供給導管、 9,10 圧力バラ
ンサー、11,12 方向制御弁、13,14 消
費器、 15,16,17,18,19,19a,1
9b,20,20a,20b 導管、 21 交
換弁、22,22a,22b 導管、 23 需
要流調整装置、 23a ばね、 24,25,
26,27 導管、 28,29 圧力減少弁、
30,31 絞り、 32 圧力制限弁1 pump, 2 adjustment cylinder, 3 spring, 4 adjustment piston, 5 tank, 6
Discharge conduit, 6a, 6b, 6c Conduit, 7
Branch supply conduit, 7a Conduit, 7b Discharge conduit, 8 Branch supply conduit, 9,10 Pressure balancer, 11,12 Directional control valve, 13,14 Consumer, 15,16,17,18,19,19a,1
9b, 20, 20a, 20b conduit, 21 exchange valve, 22, 22a, 22b conduit, 23 demand flow adjustment device, 23a spring, 24, 25,
26, 27 conduit, 28, 29 pressure reduction valve,
30, 31 Throttle, 32 Pressure limiting valve
Claims (8)
力エネルギーを消費する複数の消費器に圧力媒体流を荷
重に無関係に分配するための制御回路であって、消費器
がそれぞれ中間位置で絞り作用を生ぜしめる方向制御弁
によって操作可能であり、方向制御弁の上流側に方向制
御弁への圧力媒体の流れを規定する圧力バランサーを接
続してあり、圧力バランサーが方向制御弁の上流側の圧
力及び方向制御弁の下流側の圧力から導かれた第1の圧
力差並びに、ポンプ圧力及び最大の負荷圧力から導かれ
た第2の圧力差に関連して作動可能である形式のものに
おて、少なくとも一方の圧力バランサー(9,10)に
おいて圧力差が調節されるようになっていることを特徴
とする、圧力媒体流を荷重に無関係に分配するための制
御回路。1. A control circuit for load-independent distribution of a flow of pressure medium to a plurality of consumers connected to a hydraulic pump and consuming hydraulic energy, each of the consumers having an intermediate position. A pressure balancer is connected upstream of the directional control valve to regulate the flow of pressure medium to the directional control valve. a first pressure difference derived from the side pressure and the pressure downstream of the directional control valve; and a second pressure difference derived from the pump pressure and the maximum load pressure. Control circuit for load-independent distribution of pressure medium flow, characterized in that the pressure difference is regulated in at least one pressure balancer (9, 10).
後の圧力から導かれた圧力、及びポンプ圧力から導かれ
た圧力によって開放方向へかつ、方向制御弁の前の圧力
から導かれた圧力、及びすべての消費器の最大の出力圧
力から導かれた圧力によって閉鎖方向へ負荷されており
、圧力バランサーに圧力のための作用面が設けられてお
り、作用面に圧力導管が通じており、少くとも1つの圧
力導管(19b,24,7a,22a;20b,26,
8a,22b)内に、圧力に影響を及ぼす装置(28;
30,7,31,32)が接続されている請求項1記載
の制御回路。2. Pressure derived from the pressure after the directional control valve to which the pressure balancer belongs and pressure derived from the pump pressure in the opening direction and from the pressure in front of the directional control valve; and is loaded in the closing direction by a pressure derived from the maximum output pressure of all the consumers, the pressure balancer is provided with a working surface for the pressure, a pressure conduit leads to the working surface, and a small one pressure conduit (19b, 24, 7a, 22a; 20b, 26,
8a, 22b), a pressure influencing device (28;
30, 7, 31, 32) are connected to the control circuit according to claim 1.
(28)として構成されている請求項2記載の制御回路
。3. Control circuit according to claim 2, wherein the device for influencing the pressure is constructed as a pressure reduction valve (28).
請求項3記載の制御回路。4. Control circuit according to claim 3, wherein the pressure reduction valve (28) is adjustable.
ある請求項4記載の制御回路。5. Control circuit according to claim 4, wherein the pressure reduction valve (28) is remotely controllable.
)を有しており、絞りの下流側から排出導管(7b)が
分岐しており、この分岐導管内に絞り(31)が設けら
れており、この絞り(31)の下流側に圧力制限弁(3
2)が接続されている請求項2記載の制御回路。[Claim 6] The device that affects the pressure is a constrictor (30
), a discharge pipe (7b) branches from the downstream side of the throttle, a throttle (31) is provided in this branch pipe, and a pressure limiting valve is installed downstream of this throttle (31). (3
3. The control circuit according to claim 2, wherein: 2) is connected to the control circuit.
,7b,31,32)がポンプに通じる導管(7a)内
に配置されており、この導管が1つの消費器(13)の
圧力バランサー(9)の作用面に通じている請求項2か
ら6のいずれか1項記載の制御回路。Claim 7: Device for influencing pressure (28; 30
, 7b, 31, 32) are arranged in a conduit (7a) leading to the pump, which conduit leads to the working surface of the pressure balancer (9) of one consumer (13). The control circuit according to any one of .
大の消費器圧力を導く導管(22b)内に配置されてお
り、この導管が1つの消費器(14)の圧力バランサー
(10)の作用面に通じている請求項2から7のいずれ
か1項記載の制御回路。8. A pressure influencing device (29) is arranged in the conduit (22b) leading to the maximum consumer pressure, which conduit is connected to the pressure balancer (10) of one consumer (14). 8. A control circuit according to any one of claims 2 to 7, which communicates with the working surface.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4036720A DE4036720C2 (en) | 1990-11-17 | 1990-11-17 | Control circuit for the load-independent distribution of a pressure medium flow |
DE4036720.7 | 1990-11-17 |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH04266603A true JPH04266603A (en) | 1992-09-22 |
Family
ID=6418480
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP3301496A Pending JPH04266603A (en) | 1990-11-17 | 1991-11-18 | Control circuit for distributing pressure medium flow regardless of load |
Country Status (4)
Country | Link |
---|---|
US (1) | US5237908A (en) |
JP (1) | JPH04266603A (en) |
KR (1) | KR920010388A (en) |
DE (1) | DE4036720C2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1994010456A1 (en) * | 1992-10-29 | 1994-05-11 | Hitachi Construction Machinery Co., Ltd. | Hydraulic control valve device and hydaulically driving device |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2694605B1 (en) * | 1992-08-04 | 1994-11-10 | Bennes Marrel | Control assembly for a plurality of hydraulic receivers. |
EP0747601B1 (en) * | 1992-10-23 | 2000-04-12 | Kabushiki Kaisha Komatsu Seisakusho | Pressure oil supply system having a pressure compensating valve |
DE4341244C2 (en) * | 1993-12-03 | 1997-08-14 | Orenstein & Koppel Ag | Control for dividing the flow rate made available by at least one pump in hydraulic systems among several consumers |
JP3165785B2 (en) * | 1996-03-29 | 2001-05-14 | ジャクティ・エンジニアリング株式会社 | Jaw crusher |
US5699665A (en) * | 1996-04-10 | 1997-12-23 | Commercial Intertech Corp. | Control system with induced load isolation and relief |
DE19615593B4 (en) * | 1996-04-19 | 2007-02-22 | Linde Ag | Hydrostatic drive system |
DE19640100B4 (en) * | 1996-09-28 | 2005-07-14 | Sauer-Danfoss Holding Aps | Hydraulic system |
DE19740579A1 (en) * | 1997-09-16 | 1999-03-18 | Mannesmann Rexroth Ag | Hydraulic device |
FR2807118B1 (en) * | 2000-03-28 | 2002-07-05 | Mannesmann Rexroth Sa | HYDRAULIC CIRCUIT FOR OPERATING MULTIPLE HYDRAULIC RECEIVERS |
DE102007014550A1 (en) * | 2007-03-27 | 2008-10-09 | Hydac Filtertechnik Gmbh | valve assembly |
DE102007054134A1 (en) * | 2007-11-14 | 2009-05-20 | Hydac Filtertechnik Gmbh | Hydraulic valve device |
DE102008038381B4 (en) | 2007-12-19 | 2018-12-27 | Linde Hydraulics Gmbh & Co. Kg | Hydrostatic drive system |
ITBO20100358A1 (en) * | 2010-06-08 | 2011-12-09 | Hydrocontrol S P A Con Unico Socio | HYDRAULIC PLANT AND HYDRAULIC DISTRIBUTOR FOR THE OPERATION OF OPERATING MACHINES |
DE102011011138A1 (en) * | 2011-02-14 | 2012-08-16 | Linde Material Handling Gmbh | Hydrostatic drive system |
CN105221506B (en) * | 2015-09-18 | 2017-08-25 | 徐州工业职业技术学院 | A kind of load-sensitive valve and load-sensitive hydraulic system |
DE102018202148B3 (en) * | 2018-02-12 | 2019-03-07 | Hawe Hydraulik Se | Hydraulic valve assembly with forced switching and mobile hydraulic system |
KR102502268B1 (en) * | 2022-12-08 | 2023-02-23 | 대한민국 | Experimental facilities for realizing flooded situations |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3982469A (en) * | 1976-01-23 | 1976-09-28 | Caterpillar Tractor Co. | Apparatus for controlling work element operating pressures in a fluid system |
DE3422165A1 (en) * | 1983-06-14 | 1984-12-20 | Linde Ag, 6200 Wiesbaden | Hydraulic arrangement with a pump and at least two consumers of hydraulic energy acted upon by this pump |
DE3321483A1 (en) * | 1983-06-14 | 1984-12-20 | Linde Ag, 6200 Wiesbaden | HYDRAULIC DEVICE WITH ONE PUMP AND AT LEAST TWO OF THESE INACTED CONSUMERS OF HYDRAULIC ENERGY |
DE3841507C1 (en) * | 1988-01-22 | 1989-06-29 | Danfoss A/S, Nordborg, Dk | |
DE68910940T2 (en) * | 1988-05-10 | 1994-04-21 | Hitachi Construction Machinery | HYDRAULIC DRIVE UNIT FOR CONSTRUCTION MACHINERY. |
US5067389A (en) * | 1990-08-30 | 1991-11-26 | Caterpillar Inc. | Load check and pressure compensating valve |
-
1990
- 1990-11-17 DE DE4036720A patent/DE4036720C2/en not_active Expired - Fee Related
-
1991
- 1991-11-12 US US07/791,570 patent/US5237908A/en not_active Expired - Fee Related
- 1991-11-15 KR KR1019910020309A patent/KR920010388A/en not_active Application Discontinuation
- 1991-11-18 JP JP3301496A patent/JPH04266603A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1994010456A1 (en) * | 1992-10-29 | 1994-05-11 | Hitachi Construction Machinery Co., Ltd. | Hydraulic control valve device and hydaulically driving device |
US5433076A (en) * | 1992-10-29 | 1995-07-18 | Hitachi Construction Machinery Co., Ltd. | Hydraulic control valve apparatus and hydraulic drive system |
Also Published As
Publication number | Publication date |
---|---|
US5237908A (en) | 1993-08-24 |
DE4036720A1 (en) | 1992-05-21 |
DE4036720C2 (en) | 2001-09-13 |
KR920010388A (en) | 1992-06-26 |
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